CN107002811A - Changing load control system in hydraulic means - Google Patents
Changing load control system in hydraulic means Download PDFInfo
- Publication number
- CN107002811A CN107002811A CN201580051445.5A CN201580051445A CN107002811A CN 107002811 A CN107002811 A CN 107002811A CN 201580051445 A CN201580051445 A CN 201580051445A CN 107002811 A CN107002811 A CN 107002811A
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- CN
- China
- Prior art keywords
- hydraulic means
- piston
- upper tubular
- support member
- control system
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
- F16F9/19—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein with a single cylinder and of single-tube type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/005—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper
- F16F13/007—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper the damper being a fluid damper
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
- F16F9/3214—Constructional features of pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
- F16F9/49—Stops limiting fluid passage, e.g. hydraulic stops or elastomeric elements inside the cylinder which contribute to changes in fluid damping
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
The present invention relates to a kind of hydraulic means, it includes tubular shell, the tubular shell accommodates bar, piston is fixed to the bar, the piston will be filled with lower area and the upper area separation of hydraulic fluid, so that piston and bar relatively and are axially movable together on the inside of tubular shell, hydraulic fluid passes through the inner side of tubular shell with the volume changed, from a space to another space.Described device also includes being arranged in the modular mechanism on the inside of lower space so that by means of the modular mechanism, adjust in the end of the maximum compression of hydraulic means and the also damping in other relative positions.
Description
Technical field
As described in the title in this specification, the present invention relates to the changing load control system in hydraulic means,
It adjusts hydraulic load development during being directed at least arbitrary period when device is in operation.
The system is applied to the hydraulic means of such as damper, so that the first stroke for helping to reduce under maximum compression is whole
The problem of emergentness produced during the second stroke ends after only and under maximum extension so that especially in hydraulic means
Each stroke, the first stroke and the sudden reduction of the two stroke termination control.
Therefore, system of the invention is intended to when hydraulic means is towards during maximum extension motion and when it is towards maximum compression
There is provided the damping for hydraulic means when being moved along relative direction, the damping depends on inscribing when each the length of damper
Degree, and depending on the linear speed of the damper when damper starts.
It should also be emphasized that the system of the present invention allows the scope of the wide in range of geometrical construction, layout and material and change,
So that it is guaranteed that it is according to the boundary condition and the adaptability of size each applied and the simplification of configuration.
Therefore, the mechanism of the hydraulic means of the hydraulic compression retainer of the damper of vehicle is carried for present invention selection.
Background technology
Currently, some hydraulic means of such as damper include two parts fitted together.
Part I includes piston-bar assembly, and Part II includes housing, it is characterised in that exist in hydraulic fluid
In the case of be enough the tubular for allowing piston-bar assembly in its interior Slideslip（tube cylindrical）.
The component allows the Union Movement for making component to tubular shell（joint movement）Depart from component to piston-bar
The Union Movement of component so that hydraulic part, which can or partially or fully be filtered out, wishes to be prevented from from a component transmission
To the frequency of another component.
The geometry limitation of the physical environment operated wherein based on damper, the maximum that piston can advance in case inside
Distance（The stroke of damper）It is limited.In some devices, the limitation is realized by means of mechanical stopping piece：
- when the minimum length of damper is by limited time, these retainers are referred to as compression stops, maximum compression retainer etc..
- when the maximum length of damper is by limited time, these retainers are referred to as resilience retainer, maximum extension retainer
Deng.
In some applications of damper, due to lacking comfortableness, excessive noise, due to continuous using caused abrasion
Deng the emergentness relatively of these mechanical arresting devices can be undesirable.
The content of the invention
In order to reach the problem of being referred in the paragraph of target and solution above, the present invention provides variable in hydraulic means
Load control system, wherein, hydraulic means includes tubular shell, wherein, bar is attached to piston with linking, and the piston will be filled
The lower area and upper area for having hydraulic fluid are separated so that when piston and bar are moved, two parts are in tubular shell
Side is advanced together relative to axis along both direction, so that the hydraulic fluid on the inside of tubular shell is from a region shifting to another
One region, therefore change the volume of area inside；Wherein, piston is moved in hydraulic means towards compression,metal-to-metal position, piston
The volume of lower area is gradually reduced towards this motion of compression,metal-to-metal position, and hydraulic means is also when it is in maximum extend
Resting position is taken during place.
It includes the modular mechanism on the inside of the lower area of tubular shell, with lid sealing at bottom.
Upper area and lower area are connected by a series of through holes in piston.
Modular mechanism includes upper tubular head, and lower tube is coordinated and guided in the upper tubular head, and
And wherein, annular support member coordinate on its bottom, when upper tubular head towards hydraulic means compression,metal-to-metal position to
During lower traveling, and when its maximum extended position along relative direction towards hydraulic means is travelled upwardly, upper tubular head
Along axial-movement.
Upper tubular head has a series of through holes on its wall, the through hole connection internal chamber and outer annular chamber
Room, the internal chamber is closed by upper tubular head and the inner side of lower tube, and the outer annular chamber is by tubular shell
Inner side and the closing of upper tubular head and the outside of lower tube.
Annular support member has a series of through holes, the through hole connection annular support member and outer annular chamber.
In one embodiment, the through hole of annular support member meets disk towards being attached to before lid（frontal disc）；Its
In, through hole and the combination restriction valve gear for before meeting disk, when meeting disk before the downside touching of annular support member, valve gear regulation liquid
Press path of the fluid by the through hole.
In the alternate embodiment of one embodiment described in paragraph above, without using preceding meeting disk so that ring
The through hole of shape support member is towards lid；Wherein, the combination of through hole and lid limits valve gear, is met when before the downside touching of annular support member
During disk, valve gear regulation path of the hydraulic fluid by through hole.
Annular support member is mated the inner face against tubular shell.
One of downside of annular support member includes the lower concave part that through hole leads in it, while the upside of annular support member
The upper recess that bottom including lower tube is mated thereto.
The through hole on upper tubular head includes a series of through slots, and it extends to the lower edge on upper tubular head.
In one embodiment, the upper tubular head of modular mechanism links with piston, while in another alternative reality
Apply in example, the upper tubular head of modular mechanism and piston are two parts being independently and separately.
In one embodiment, modular mechanism is supplemented with compression coaxial springs.Compress the end abutment ring of coaxial springs
A series of radial extensions on shape support member and adjacent upper tubular head.A series of this radial extension be mated against
The inner side of tubular shell so that when coaxial springs tend to make upper tubular head move upwards along axis, when upper tubular head
When portion overcomes the resistance of coaxial springs to travel down to the compression,metal-to-metal position of hydraulic means, and when upper tubular head is along phase
To direction towards the maximum extended position of hydraulic means travel upwardly when, upper tubular head can advance along axis, and
Wherein, on the inside of the externally-located annular compartment of coaxial springs.
Bar includes lower extension, and it is reached below piston, and in this place, in some positions of dampening arrangement, this is downward
Extending portion loosely coordinates on the inside of lower tube, wherein, loose fit limits the annular channels of hydraulic fluid.
Upper tubular head includes tapered upper mouth.
In one embodiment, the upper header of annular mechanism includes certain area, and the region is carried compared to its company
The region of the piston being connected to lower case hardness so that when piston part and upper tubular head close to each other when therebetween
Initial contact is buffered by the region of more soft.
According to the content described in previous paragraph, the area with lower case hardness is by being attached to upper tubular head
Top edge annular body determine.
On the embodiment without coaxial springs, the component of lower tube and annular support member is attached to pipe by interference fit
Shape housing, so that annular support member is fixed into tubular shell so that in this case, after operation circulation, it is not necessary to same
Axle spring come recover the present invention system home position.
Therefore, when hydraulic means is operated with manner described below, reducing the problem of caused by stopping suddenly
In, changing load control system of the invention plays the effect of key.
The piston of hydraulic means is touched on upper tubular head, and sends signal so that it starts operation to system.
Before meet disk and constitute valve gear together with the through hole of annular support member, it adjusts the path that fluid passes in and out the through hole, should
Path leads to coaxial exterior chamber.
Through slot on the wall on upper tubular head is according to the relative position between lower tube and upper tubular head
Cross section path of the hydraulic fluid by them is controlled, upper tubular head is the part advanced relative to lower tube.
The coaxial springs that annular support member and upper tubular head are assembled into by interference fit have operation circulation it
The target that system returns it to its original state is restarted afterwards.
Therefore, because the system of the present invention, it may be possible to provide relative to the damping of the length and speed of damper.Further
Ground, it, which is designed, allows the scope of the wide in range of geometrical construction, layout and material and change, so that it is guaranteed that it is according to the side each applied
The adaptability of boundary's condition and size and the simplification of configuration.
Hereinafter, specification is best understood from order to provide, details the present invention's in a series of accompanying drawings
Object, accompanying drawing be specification must part and be in order at the purpose of diagram and do not limit.
Brief description of the drawings
Fig. 1 shows to include the elevational cross-section of the hydraulic means of the changing load control system as the purpose of the present invention
Figure.Hydraulic means is the damper in maximum extended position.
Fig. 2 is shown similar to the cross-sectional elevational view of the hydraulic means of a hydraulic means in Fig. 1, wherein, damper
In the position close to its maximum extension.
Fig. 3 is shown similar to the view of previous hydraulic means, wherein, damper is in an intermediate position.
Fig. 4 shows that wherein damper is in the cross-sectional elevational view close to its compression,metal-to-metal position.
Fig. 5 represents the viewgraph of cross-section of the damper designed according to second embodiment, and it is with showing in previous accompanying drawing
First embodiment has several places different.
Fig. 6 shows the viewgraph of cross-section of the damper designed according to 3rd embodiment, and it has with previous accompanying drawing
It is different.
Fig. 7 shows the perspective view for the modular mechanism being seated under the piston for being attached to bar in tubular shell, the work
Plug is advanced when damper is operated on the inside of tubular shell along axis along both direction.
Fig. 8 shows the perspective view of the modular mechanism also shown in previous accompanying drawing.
Fig. 9 shows the viewgraph of cross-section of the damper designed according to fourth embodiment, and it is realized with less geometry part.
Embodiment
In view of the numbering used for accompanying drawing, the changing load control system in hydraulic means is characterised by retouching
State the middle following term used：
1 tubular shell
2 modular mechanisms
3 bars
3a lower extensions
4 pistons
4a peripheral skirts
5 first upper areas
6 second lower areas
7 lids
8 insertions are perforated（Hole）
9 annular grooves
10 upper tubular heads
10a radial extensions
11 lower tubes
12 annular support members
12a upper recess
12b lower concave parts
13 coaxial springs
Disk is met before 14
15 through holes
16 outer annular chambers
17 internal chambers
18 tapered upper mouths
19 through slots
Protuberance on 20
21 annular channels
22 main bodys
Level on 23
24 annular bodies.
The hydraulic means shown on accompanying drawing is the damper being seated in vertical position, and it includes tubular shell（1）, module
Change mechanism（2）Positioned at the tubular shell（1）Interior, it, which has to be attached to, is seated in bar（3）The piston of top（4）Bar（3）, it is living
Plug（4）By piston（4）First upper area of top（5）And piston（4）Second lower area of lower section（6）Separate, and its
In, modular mechanism（2）Component be located at second lower area（6）In.
In modular mechanism（2）Lower section and closure tubular shell（1）, lid（7）It is matched with the tubular shell（1）Bottom
Portion.
Aforementioned areas（Upper area（5）And lower area（6））Via piston（4）On a series of insertions perforation（Hole）
（8）Connection, a series of insertion perforation（8）The hydraulic fluid when damper is operated is allowed to pass through.
Piston（4）Including peripheral skirt（4a）, its outside is mated against tubular shell（1）Inner side, and periphery skirt
Portion（4a）The outside also have a series of annular grooves（9）.
In one embodiment, piston（4）Slave module mechanism（2）Separate, and it is not attached together, while another
In embodiment, piston（4）Pass through foregoing piston（4）Peripheral skirt（4a）It is connected to modular mechanism（2）.
Work as piston（4）Slave module mechanism（2）Separation and its when not being attached together, in one embodiment, upper tube
Shape head（10）Including with than piston（4）The lower case hardness of material hardness region so that work as piston（4）And module
Change mechanism（2）When being moved closer to together untill it is contacted, outer skirt（4a）With upper tubular head（10）
Between this initial contact be soft, buffer-type（cushioned）Contact, which improve the operation of hydraulic means.
To achieve it, in one embodiment, the region with more soft is by being attached to upper tubular head
（10）Top edge annular body（24）It is determined that.
As being shown more clearly that on Fig. 7 and 8, modular mechanism（2）Including upper tubular head（10）, lower tube
（11）Coordinated and guided wherein, and annular support member（12）Coordinate in lower tube（11）Bottom on.Modularization machine
Structure（2）By being connected to annular support member on two ends（12）Be connected to upper tubular head（10）On a series of radial directions
Extension（10a）Compression coaxial springs（13）Complete.The radial extension（10a）With synthesis against tubular shell（1）'s
Inner side, to ensure to work as coaxial springs（13）Tend to make upper tubular head（10）When being moved upwards along axis, when upper tubular head
Portion（10）Overcome coaxial springs（13）Resistance overcome coaxial springs when traveling down to the compression,metal-to-metal position of damper（13）
Resistance, and when upper tubular head（10）When being advanced along the maximum extended position of relative direction direction, upper tubular head
（10）Can be in tubular shell（1）Inner side along axis exactly（with precision）Advance.
Annular support member（12）With the first upper recess（12a）（Lower tube（11）Bottom coordinate in this place）, and face
Disk is met forward（14）The second lower concave part（12b）, it is preceding to meet disk（14）It is attached to lid（7）, so as to close tubular shell（1）Bottom
Portion.
Annular support member（12）Also a series of through holes are contained（15）, it connects the annular support member（12）Lower concave part
（12b）With lower tube（11）The outer annular chamber in outside（16）So that the outer annular chamber（16）By tubular shell（1）
Inner face and upper tubular head（10）And lower tube（11）Outside closing.It is worth noting that, modular mechanism（2）It is same
Axle spring（13）Externally-located annular compartment（16）Inner side.
Outer annular chamber（16）By internal chamber（17）Supplement, the internal chamber（17）By upper tubular head（10）
And inner tube（11）Interior face closure.The part has the tapered upper mouth in upside down position（18）.
In modular mechanism（2）Some positions in, as will be described later, annular support member（12）Lower concave part
（12b）Bottom contiguous before meet disk（14）,（At least）It is partially blocked by annular support member（12）Through hole（15）.Therefore, when subtracting
Shake device is advanced towards compression,metal-to-metal position and when reducing its length, hydraulic fluid turnover through hole（15）It is current will suffer restraints or
Even it is stopped.
Upper tubular head（10）A section of wall there are a series of through slots（19）, it allows in upper tubular head
Portion（10）And lower tube（11）Between some relative positions in hydraulic fluid in outer annular chamber（16）And internal chamber
（17）Between pass through, when damper is seated in maximum extended position, work as coaxial springs（13）It is static, fully extended and do not have
During tension force, reach that maximum cross section is flowed.
By contrast, in the compression,metal-to-metal position of damper, through slot（19）Total length face toward pipe（11）So that
Hydraulic fluid passes in and out through slot（19）Cross sectional flow be zero.In this case, when hydraulic fluid reaches annular support member
（12）Lower concave part（12b）Bottom when, by by preceding meeting disk（14）The limitation of application makes hydraulic fluid be constrained in annular brace
Part（12）Through hole（15）Cross section path.
It is emphasized that when damper is close to compression,metal-to-metal position, leading to piston（4）The upper area of top（5）
Interior internal chamber（17）And outer annular chamber（16）Between the cross section path of fluid gradually decrease.By means of valve gear
This reduction of the path of hydraulic fluid is realized, wherein valve gear is by annular support member（12）Through hole（15）With towards the ring
Shape support member（12）Lower concave part（12b）Before meet disk（14）Combination determine, wherein the through hole（15）Lead to described recessed
Portion（12b）.
When damper reaches its maximum compression, upper tubular head（10）Lower edge contact annular support member（12）,
Annular support member（12）Correspondingly also contact closes tubular shell（1）Bottom lid（7）.Specifically, annular support member
（12）Including upper protuberance（20）, when upper tubular head（10）During in compression,metal-to-metal position, upper tubular head（10）It is adjacent
Connect protuberance on this（20）.
In addition, bar（3）Including lower extension（3a）, it extends downwardly and reaches piston（4）Lower section so that in damper
In compression,metal-to-metal position and also in the position close to maximum compression（Fig. 4）, bar（3）The lower extension（3a）Loosely match somebody with somebody
Close in lower tube（11）Inner side.Loose cooperation limits gap, and it correspondingly limits the annular channels of hydraulic fluid（21）, and work as
When damper is close to maximum compression, auxiliary rod（3）And piston（4）The stopping of component.
The maximum extended position of damper in Fig. 1 and is also shown on Fig. 2,5 and 6.
On Fig. 1, piston（4）With upper tubular head（10）Separation, while on Fig. 5 and 6, upper header（10）Attachment
To piston（4）Skirt section（4a）.In this case, it is living as shown on Fig. 5 when damper tends to recover maximum extended position
Plug（4）Upward motion pull modular mechanism（2）Component it is therewith upward so that with lid（7）And also with preceding meeting disk
（14）Separation.In other situations, piston（4）Simply pull on upper tubular head（10）It is therewith upward.
According to Fig. 1, when damper tends to recover maximum extended position, piston（4）Do not pull modular mechanism（2）With it
It is upward together so that in this case, upper tubular head（10）By means of coaxial springs（13）Return to maximum extended position.
Work as bar（3）And piston（4）When component travels down to compression,metal-to-metal position, upper tubular head（10）Overcome coaxial
Spring（13）Resistance travel downwardly, be gradually reduced outer annular chamber（16）And internal chamber（17）Between by means of top
Tubular head（10）Through slot（19）Hydraulic fluid path, and wherein, hydraulic fluid is from internal chamber（17）Advance
To piston（4）First upper area of top（5）.The current of hydraulic fluid flows in and out annular support member（12）Through hole
（15）, through hole（15）It is valve gear（2）A part, valve gear（2）By these through holes（15）With preceding meet disk（14）Combination structure
Into.
In piston（4）Decline terminal stage in, bar（3）Lower extension（3a）Into lower tube（11）, so that with
The path of hydraulic fluid has further been constrained in mode explained above.
By contrast, when damper is by coaxial springs（13）The auxiliary of tension force when advancing to maximum extended position, pump
Pu effect causes hydraulic fluid from piston（4）First upper area of top（5）It flow to the second lower area（6）, modularization
Mechanism（2）Component, internal chamber（17）And outer annular chamber（16）At this.
Before meet disk（14）By means of main body（22）Attach to lid（7）.
It is worth noting that, annular support member（12）It is mated against tubular shell（1）Inner face.
Depending on for example in the modular mechanism shown on Fig. 1（2）Position, during the compression stroke of damper, bar
（3）It will travel downwardly.Therefore, in modular mechanism（2）At the time of beginning before operation, bar（3）In certain position so that living
Plug（4）Skirt section（4a）Do not touch modular mechanism（2）Any part.That is, when the system starts operation, piston
（4）Skirt section（4a）In on（to）The upper level of inlet point（23）The tubular shell of top（1）Region in so that it is described
Upper level（23）With upper tubular head（10）Top edge correspondence.In this case, coaxial springs（13）By upper tubular head
Portion（10）And lower tube（11）It is maintained at maximum extended spot.Hydraulic fluid is in piston（4）To freely being moved between valve gear, its
Middle valve gear meets disk before including（14）And annular support member（12）Through hole（15）.When hydraulic means start operation when, occur with
The event of lower order.
Piston（4）Skirt section（4a）Contact upper tubular head（10）Top edge so that prevent hydraulic fluid described
Upper tubular head（10）Outside on pass through, and lower area（6）It is divided into two chambers：Internal compression chamber（17）With it is outer
Annular compression chamber of portion（16）.
Internal chamber（17）By piston（4）Interior zone, skirt section（4a）Internal diameter, upper tubular head（10）It is tapered
Upper mouth（18）, lower tube（11）Inner side, annular support member（12）Inner area and before meet disk（14）It is limited on upside.
Internal chamber（17）In, as in the normal operating of damper, hydraulic fluid is from piston（4）Path to valve gear is protected
Hold and do not change.
Outer annular chamber（16）By piston（4）Skirt section（4a）Outside and bottom, upper tubular head（10）Top
Outer surface, lower tube in portion part（11）Outside, annular support member（12）Perimeter and tubular shell（1）Inner side
It is limited on upside.
In outer annular chamber（16）In, the path of fluid is by means of upper tubular head（10）Through slot（19）And ring
Shape support member（12）Through hole（15）Reach internal chamber（17）.Initially, annular support member（12）Through hole（15）By being attached
To closure tubular shell（1）Bottom lid（7）Before meet disk（14）Completely or partially close.
It is probably following situation, depending on design, on the upper tubular head（10）Internal diameter and lower tube（11）'s
There is no any interference between external diameter（interference）In the case of, peripheral skirt（4a）Contact upper tubular head（10）'s
Top edge.In this case, bar is worked as（3）And piston（4）When component is travelled downwardly, piston（4）Peripheral skirt（4a）With top
Tubular head（10）Connection.
Piston（4）Skirt section（4a）Promote upper tubular head（10）Top edge, force it to travel downwardly and compress same
Axle spring（13）.The compression of damper is higher, upper tubular head（10）Decline it is lower, and therefore, upper tubular head
（10）And lower tube（11）Between block（shut-off）Interference is bigger so that turnover through slot（19）With upper tubular head
（10）Cross sectional flow gradually decrease.
Initially, valve gear almost stops hydraulic fluid turnover annular support member completely（12）Through hole（15）Path,
So that outer annular chamber（16）The hydraulic fluid of inner side is towards internal chamber（17）Jet away from through slot（19）.When transversal
When face path is reduced, outer annular chamber（16）In pressure increase.
The initial soft damping of control measure generation, its load depends on the position of damper（On passing through through slot
（19）Higher or lower cross section path and speed）, this generation is the power of the chi square function of speed.
Work as through slot（19）Cross sectional flow it is sufficiently small when, the enough pressure of injection generation of hydraulic fluid is closed with overcoming
The resistance of the valve gear of conjunction, and wherein, pressure opens annular support member in a controlled manner（12）Through hole（15）.
The control measure couple with a previous measure, prevent load as speed increases and excessively increase.Correction is carried
The chi square function of lotus curve.In this way, for the same position of the damper of the area inside, the linear increase of load
It is actually proportional to speed.
Work as lower tube（11）Stop through slot completely（19）When, the unique channel that hydraulic fluid leaves is annular support member
（12）Through hole（15）.Now, when valve gear is opened completely, the increase of load turns into chi square function again.However, region or
Cross section path is sufficiently wide so that the effect of chi square function is hardly obvious.In fact, most significant aspect is that maximum is carried
Lotus point slightly shifts to an earlier date with speed, and when occurring strong compression, this provides additional advantage.
In barrier structure（block structure）In the situation of design（When upper tubular head（10）Bottom connect
It is connected to annular support member（12）When）, by means of transmitting power with lower component chain：Piston（4）, upper tubular head（10）With annular branch
Support member（12）.Upper tubular head（10）Bottom touching annular support member（12）, so that with before meeting disk（14）Stop through hole
（15）, this is in outer annular chamber（16）Middle generation hydraulic lock.If this excessive pressure is because how it influences piston
（4）And annular support member（12）And cause it to be out of favour, then using the conventional components of mechanical stopping piece.
When stroke of the damper initially towards maximum extended position, bar（3）Travel upwardly so that piston（4）Skirt section
（4a）Stop upper tubular head（10）On pressure.Outer annular chamber（16）Stop reducing and starting increase so that pressure
Decline, and the flow inversion of hydraulic fluid, so as to allow valve gear to close through hole（15）.Outer annular chamber（16）On pressure
It is decreased up to equal to internal chamber（17）On pressure untill, and piston（4）With upper tubular head（10）Separation, so as to permit
Perhaps hydraulic fluid is on upper tubular head（10）Outer surface and tubular shell（1）Inner side between pass through.
Coaxial springs（13）Tend to decompress and return to its equilbrium position.Because it in every an end portion passes through interference fit group
It is attached to upper tubular head（10）And annular support member（12）, and simultaneously, the annular support member（12）It is assembled into tubular shell
（1）, therefore entirely component reaches resting position and not moved.
When damper starts to compress or extends, and the current direction reversely and when valve gear is turned off of hydraulic fluid, direction
Outer annular chamber（16）Flow through annular support member（12）Through hole（15）With upper tubular head（10）Through slot
（19）Occur, unless these are by inner tube（11）Fully stop.
Due to the insufficient flow by these paths with by hydraulic fluid from internal chamber（17）It is fed to outer annular chamber
Room（16）, therefore by the fact that auxiliary coaxial springs（13）Action：Piston（4）Than upper tubular head（10）Climb
Faster and it is drawn up, this is in outer annular chamber（16）Middle generation low pressure so that upper tubular head（10）Braking and
From piston（4）Lightly separate, so as to allow hydraulic fluid to enter.Upper tubular head（10）Follow piston（4）Until it is arrived
Untill resting position.
It is emphasized that as the situation as non-limiting example in figures 7 and 8 shown in as, depending on bar（3）
Axis rotation generation design basic geometry.However, this is not enforceable, because net shape will depend on the phase
The modification in the region of prestige, and depending on other specific requirements, weight, resistance, inertia etc..One advantage of current design
Be, final products can a part be made with connecing a part, to optimize the continuous control of traffic areas.Thus,
Observe following characteristics：
For the present invention, the component of valve gear is vital, because different from other inventions of similarity, control
The brake pressure of compression stops is configured depending on it.In the sense that, the geometrical construction of valve gear is not exclusively limited to
Content shown in accompanying drawing.
It can be made up of one or more valve gears, and its resistance accumulated will dominate the behavior of compression stops.
It can include the different geometrical constructions for through hole and groove, or generally, auxiliary hydraulic pressure fluid is propped up towards annular
Support member（12）Any kind of groove of the mode of flowing.
It can use distinct methods（Punching press, sintering, machining etc.）And use can be resisted and generated during operation
Stress any material（Steel, bronze, aluminium etc.）Build.
Upper tubular head（10）With the function that load is changed depending on its position.Again, its geometrical construction is not
Exclusively it is limited to the content shown in accompanying drawing.
Upper tubular head（10）Through slot（19）It can be designed to carry one or more grooves, hole or window, and
And generally, with helpful cross section path with upper tubular head（10）And lower tube（11）Between interference region increase
And the mode changed（way）Any kind of groove, so as to produce carry higher or lower emergentness（abruptness）Enter
Enter.
It can be formed with metal, composite or plastics, and this depends on made groove or the stress and complexity in hole.
Lower tube（11）Little by little stop upper tubular head（10）Through slot（19）.However, because it can include
It is connected to internal chamber（17）And outer annular chamber（16）Groove, therefore its geometrical construction needs not be completely solid
（solid）So that the change of load produces higher or lower emergentness.
Annular support member（12）Keep valve gear and before meet disk（14）Combination.Again, its geometrical construction is not exclusively
The content shown in accompanying drawing is limited to, and various grooves can be included, to work as outer annular chamber（16）In pressure force valve
Device controls load change when opening the path of hydraulic fluid.
As shown on Fig. 9, the multi-functional of system of the invention allows annular support member（12）Disk is met before not needing
（14）In the case of be directly positioned on lid（7）On, and wherein annular support member（12）And lid（7）Including necessary groove to control
Load.It also can be in not all or part of annular support member for being included in the part to form valve gear（12）And lid
（7）Between geometry part in the case of realize.
Coaxial springs（13）It is responsible for making component return to its original state, and load is provided depending on position.In order to optimize
How to adjust hydraulic load and component is returned to its original state, coaxial springs（13）Can have constant or variable
Resistance, and constituted by there is optional line in terms of shapes and sizes, or by a series of rings.It can by interference fit or
Person coordinates also by way of additional components.
However, as shown on Fig. 6, working as upper header（10）It is attached to piston（4）Skirt section（4a）When, there is also wherein not
Use coaxial springs（13）Embodiment.
Accordingly, with respect to no coaxial springs（13）Embodiment, lower tube（11）And annular support member（12）Component lead to
Cross interference fit and be connected to tubular shell（1）, so that by annular support member（12）Fixed to tubular shell（1）So that in the feelings
In shape, after operation circulation, it is not necessary to coaxial springs（13）To recover the home position of system of the invention.In the situation
In, upper tubular head（10）It is connected to piston（4）Outer skirt（4a）.
Then the content summarized in previous paragraph, is next attached to the upper tubular head（10）Piston（4）'s
Motion, works as lower tube（11）Top enter upper tubular head（10）Lower inside when, hydraulic means start operation.
The multi-functional and many possible design of the present invention is given, the component can be used in difference for various applications
In position.For damper, the present invention can be used as hydraulic compression retainer or hydraulic pressure resilience retainer.It is for any
All it is effective for single tube or two-tube technology, and can be installed in the main body of damper or in neighbouring main body, example
Such as, in the storage chamber of hydraulic fluid.
Roughly, the present invention is applied to be designed to any hydraulic means of a part for structure（Mobile or fixed
Both）, with when stroke is in structure（Solar panel, for metal structure of building etc.）In or vehicle in occur when there is provided
The mechanical-hydraulic of stroke is terminated.
Claims (15)
1. the changing load control system in hydraulic means, wherein, the hydraulic means includes tubular shell, wherein, bar attachment
To piston, the lower area and upper area that the piston will be filled with hydraulic fluid are separated so that when the piston and described
When bar is moved, the bar and the piston are advanced together on the inside of the tubular shell relative to axis, so that the tubulose
The hydraulic fluid of case inside changes the volume of the area inside from a region shifting to another region；Wherein, institute
State piston to move towards compression,metal-to-metal position in the hydraulic means, so as to be gradually reduced the volume of the lower area；When
When the hydraulic means is in maximum extended spot, it further takes resting position；
It is characterized in that：
- the system includes being located at the tubular shell（1）Lower area（6）The modular mechanism of inner side（2）, the tubulose
Housing（1）In bottom（7）Place's lid sealing；
- the upper area（5）With the lower area（6）Pass through the piston（4）In a series of insertions perforation（8）Even
Connect；
- the modular mechanism（2）Including upper tubular head（10）, lower tube（11）Coordinated and guided wherein, and
Annular support member（12）Coordinate on its bottom, when being travelled downwardly in the hydraulic means towards compression,metal-to-metal position and
When the maximum extended position towards the hydraulic means is travelled upwardly along relative direction, the upper tubular head（10）Have
Axial mobility；
- upper tubular the head（10）With a series of through slots on its wall（19）, the through slot（19）In connection
Portion's chamber（17）With outer annular chamber（16）, the internal chamber（17）By the upper tubular head（10）With the bottom
Pipe（11）Inner side closing, the outer annular chamber（16）By the tubular shell（1）Inner side and the lower tube（11）
With the upper tubular head（10）Outside limit；And,
- the annular support member（12）With a series of through holes（15）, it connects the annular support member（12）With the outside
Annular compartment（16）.
2. the changing load control system in hydraulic means according to claim 1, it is characterised in that the annular brace
Part（12）Through hole（15）Towards being attached to the lid（7）Before meet disk（14）；Wherein, the through hole（15）With it is described before meet disk
（14）Combination limit valve gear, when the annular support member（12）Contacts-side-down described in before meet disk（14）When, the valve dress
Put regulation hydraulic fluid and pass in and out the through hole（15）Path.
3. the changing load control system in hydraulic means according to claim 1, it is characterised in that the annular brace
Part（12）Through hole（15）Towards the lid（7）；Wherein, the through hole（15）With the lid（7）Combination limit valve gear, when
The annular support member（12）Contacts-side-down described in cover（7）When, the valve gear regulation hydraulic fluid passes in and out the through hole
（15）Path.
4. the changing load control system in the hydraulic means according to any one of precedent claims, its feature exists
In the annular support member（12）With synthesis against the tubular shell（1）Inner side.
5. the changing load control system in the hydraulic means according to any one of precedent claims, its feature exists
In the annular support member（12）Downside in one include lower concave part（12b）, the through hole（15）Lead to the lower concave part
（12b）In.
6. the changing load control system in the hydraulic means according to any one of precedent claims, its feature exists
In the annular support member（12）Upside in one include upper recess（12a）, said inner tube（11）Bottom coordinate exist
The upper recess（12a）Place.
7. the changing load control system in the hydraulic means according to any one of precedent claims, its feature exists
In the upper tubular head（10）Through slot include a series of through slots（19）, it extends to the upper tubular head
（10）Lower edge.
8. the changing load control system in the hydraulic means according to any one of precedent claims, its feature exists
In the modular mechanism（2）Upper tubular head（10）It is attached to the piston（4）.
9. the changing load control system in the hydraulic means according to any one of claim 1 to 7, its feature exists
In the modular mechanism（2）Upper tubular head（10）With the piston（4）It is two parts being independently and separately.
10. the changing load control system in the hydraulic means according to any one of precedent claims, its feature exists
In the modular mechanism（2）Also include compression coaxial springs（13）, it is connected to the annular support member on two ends
（12）Be connected on the upper tubular head（10）On a series of radial extensions（10a）, the radial extension
（10a）With synthesis against the tubular shell（1）Inner side so that when the coaxial springs（13）Tend to make the upper tubular
Head（10）When being moved upwards along the axis, when the upper tubular head（10）Overcome the coaxial springs（13）Resistance
When being moved downwardly to the compression,metal-to-metal position of the hydraulic means, and when the upper tubular head（10）Along relative direction court
When being moved upwards to the maximum extended position of the hydraulic means, the upper tubular head（10）It is axially movable, and
Wherein, the coaxial springs（13）Positioned at the outer annular chamber（16）Inner side.
11. the changing load control system in the hydraulic means according to any one of precedent claims, its feature exists
In the bar（3）Integrate lower extension（3a）, it reaches the piston（4）Lower section, wherein the dampening arrangement some
In position, the lower extension（3a）Loosely coordinate in the lower tube（11）Inner side, the loose fit limits hydraulic fluid
Annular channels（21）.
12. the changing load control system in the hydraulic means according to any one of precedent claims, its feature exists
In the upper tubular head（10）With tapered upper mouth（18）.
13. the changing load control system in hydraulic means according to claim 9, it is characterised in that the annular machine
Structure（2）Outer head（10）Region including compared to its piston being connected to carries the region of lower case hardness；
So that when the piston（4）A part and the upper tubular head（10）When approaching each other, initial contact therebetween is by more
The region buffering of soft.
14. the changing load control system in hydraulic means according to claim 9, it is characterised in that the lower table
The region of surface hardness is by being attached to the upper tubular head（10）Top edge annular element（24）It is determined that.
15. the changing load control system in hydraulic means according to claim 8, it is characterised in that the lower tube
（11）With the annular support member（12）Component by interference fit be connected to the tubular shell（1）, so that by the ring
Shape support member（12）Fixed to the tubular shell（1）.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| ESP201431107 | 2014-07-23 | ||
| ES201431107A ES2561132B1 (en) | 2014-07-23 | 2014-07-23 | VARIABLE LOAD CONTROL SYSTEM IN A HYDRAULIC DEVICE |
| PCT/ES2015/070494 WO2016012642A1 (en) | 2014-07-23 | 2015-06-25 | Variable load control system in a hydraulic device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107002811A true CN107002811A (en) | 2017-08-01 |
| CN107002811B CN107002811B (en) | 2019-08-16 |
Family
ID=55162542
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580051445.5A Active CN107002811B (en) | 2014-07-23 | 2015-06-25 | Changing load control system in hydraulic device |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US9982738B2 (en) |
| EP (1) | EP3173655B8 (en) |
| JP (1) | JP6419303B2 (en) |
| CN (1) | CN107002811B (en) |
| BR (1) | BR112017001405B1 (en) |
| ES (2) | ES2561132B1 (en) |
| WO (1) | WO2016012642A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114761701A (en) * | 2019-12-11 | 2022-07-15 | 凯迩必欧洲有限责任公司纳瓦拉分公司 | Variable load hydraulic control device |
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| FR3066796B1 (en) * | 2017-05-24 | 2019-06-21 | Peugeot Citroen Automobiles Sa | AUTO-ADJUSTABLE HYDRAULIC STOP FOR THE END OF THE RACE OF AN OSCILLATING MOVEMENT |
| IT201700061233A1 (en) * | 2017-06-05 | 2018-12-05 | Sistemi Sospensioni Spa | Hydraulic shock absorber for vehicle suspension provided with hydraulic buffer operating during the compression stroke of the shock absorber. |
| DE102018121694A1 (en) | 2017-09-07 | 2019-03-07 | Stabilus Gmbh | Systems and methods for attenuating photovoltaic module assemblies |
| US10670107B2 (en) * | 2017-12-15 | 2020-06-02 | Beijingwest Industries Co., Ltd. | Hydraulic damper with a hydraulic compression stop assembly |
| IT201800004912A1 (en) * | 2018-04-27 | 2019-10-27 | SPRING DEVICE AND VALVE UNIT FOR A BEVERAGE CONTAINER | |
| IT201800005794A1 (en) * | 2018-05-29 | 2019-11-29 | Hydraulic shock absorber for vehicle suspension equipped with a hydraulic buffer operating during the shock absorber compression stroke. | |
| US10876591B2 (en) | 2019-02-13 | 2020-12-29 | Tenneco Automotive Operating Company Inc. | Damper hydraulic compression stop cup |
| FR3093155B1 (en) * | 2019-02-21 | 2021-02-19 | Psa Automobiles Sa | HYDRAULIC SHOCK ABSORBER EQUIPPED WITH A SELF-ADAPTABLE LIMIT STOP |
| FR3094057B1 (en) * | 2019-03-22 | 2021-03-12 | Psa Automobiles Sa | SHOCK ABSORBER WITH SELF-ADAPTABLE LIMIT STOPS EQUIPPED WITH A CHAMBER IN FRONT OF A BOISSEAU |
| DE112020002358T5 (en) * | 2019-05-13 | 2022-01-27 | Tenneco Automotive Operating Company Inc. | Hydraulic compression stop with preloaded piston |
| US11181161B2 (en) | 2019-09-23 | 2021-11-23 | DRiV Automotive Inc. | Shock absorber base valve assembly |
| DE102020210809A1 (en) | 2020-08-26 | 2022-03-03 | Volkswagen Aktiengesellschaft | Shock absorber with hydraulic pressure stop and vehicle |
| US11211896B1 (en) | 2021-01-14 | 2021-12-28 | FTC Solar, Inc. | Systems for damping a solar photovoltaic array tracker |
| US11695370B2 (en) | 2021-07-27 | 2023-07-04 | FTC Solar, Inc. | Locking assembly for a solar photovoltaic array tracker |
| US20240102530A1 (en) * | 2022-09-28 | 2024-03-28 | Hitachi Astemo, Ltd. | Shock absorber |
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Also Published As
| Publication number | Publication date |
|---|---|
| EP3173655B1 (en) | 2020-03-11 |
| EP3173655B8 (en) | 2020-04-22 |
| EP3173655A8 (en) | 2017-07-12 |
| CN107002811B (en) | 2019-08-16 |
| ES2561132B1 (en) | 2016-12-19 |
| JP2017521618A (en) | 2017-08-03 |
| ES2561132A1 (en) | 2016-02-24 |
| WO2016012642A1 (en) | 2016-01-28 |
| ES2781112T3 (en) | 2020-08-28 |
| US20160025174A1 (en) | 2016-01-28 |
| JP6419303B2 (en) | 2018-11-07 |
| US9982738B2 (en) | 2018-05-29 |
| EP3173655A1 (en) | 2017-05-31 |
| BR112017001405A2 (en) | 2017-11-21 |
| EP3173655A4 (en) | 2017-08-30 |
| BR112017001405B1 (en) | 2022-09-06 |
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Address after: Xi Banyanawala Patentee after: Kaelbe Europe Limited Navarra branch Address before: Xi Banyanawala Patentee before: KYB SUSPENSIONS EUROPE, S.A. |